Double valve block and actuator assembly including same

ABSTRACT

A valve comprises a housing including a first chamber, a second chamber, and a neutral chamber. In addition, the valve comprises a stem disposed within the housing. Further, the valve comprises a first valve member at least partially disposed in the first chamber and connected to the stem and a second valve member at least partially disposed in the second chamber and connected to the stem. The first valve member has a closed position seated in a first annular valve seat and an open position spaced apart from the first valve seat. The second valve member has a closed position seated in a second annular valve seat and an open position spaced apart from the second valve seat. Moreover, the valve comprises a biasing member configured to bias the second valve member to the closed position and the first valve member to the open position.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a divisional of U.S. application Ser. No.13/179,213, filed on Jul. 8, 2011, which is incorporated herein byreference in its entirety for all purposes.

BACKGROUND

Field of the Invention

The present invention relates generally to a double valve. Moreparticularly, the present invention relates to a double valve thatallows an unpressurized port and a balance port to be in fluidcommunication when a pressurized port is closed.

Background of the Technology

In most offshore-drilling operations, a wellhead at the sea floor ispositioned at the upper end of the subterranean wellbore lined withcasing, a blowout-preventer (BOP) stack is mounted to the wellhead, anda lower-marine-riser package (LMRP) is mounted to the BOP stack. Theupper end of the LMRP typically includes a flex joint coupled to thelower end of a drilling riser that extends upward to a drilling vesselat the sea surface. A drill string is hung from the drilling vesselthrough the drilling riser, the LMRP, the BOP stack, and the wellheadinto the wellbore.

During drilling operations, drilling fluid, or mud, is pumped from thesea surface down the drill string, and returns up the annulus around thedrill string. In the event of a rapid invasion of formation fluid intothe annulus, commonly known as a kick, the BOP stack may actuate to sealthe annulus and control the fluid pressure in the wellbore. Inparticular, the BOP stack typically includes a plurality of stacked setsof opposed rams (e.g., pipe rams, shear rams, blind rams, etc.) designedto seal in the wellbore and prevent the release of high-pressureformation fluids from the wellbore and so the BOP stack and LMRPfunction as pressure control devices. The opposed rams are disposed incavities that intersect the main bore of the BOP stack and support therams as they move radially into and out of the main bore. Each set oframs is actuated and transitioned between an open position and a closedposition by a pair of actuators. In the open positions, the rams areradially withdrawn from the main bore and do not interfere with hardwarethat may extend through the main bore. However, in the closed positions,the rams are radially advanced into the main bore to close off and sealthe wellbore.

Each ram actuator hydraulically moves a piston within a cylinder to movea drive rod coupled to one of the rams. In particular, pressurizedhydraulic fluid is supplied to a first chamber within the cylinder onone side of the piston to move the piston in a first direction and closethe corresponding ram; and pressurized hydraulic fluid is supplied to asecond chamber within the cylinder on the opposite side of the piston tomove the piston in the opposite direction and open the correspondingram. For relatively deepwater subsea BOP stacks, supplying a sufficientvolume and pressure of hydraulic fluid from the surface to actuate a rammay be challenging. Consequently, in many cases, subsea-hydraulicaccumulators are employed to supply pressurized hydraulic fluid to theram actuators. The accumulators may be charged with a finite volume ofpressurized fluid at the surface prior to being deployed subsea or afterbeing deployed subsea. The pressure of the charged fluid in theaccumulators required to actuate the rams depends on a variety offactors—such as the depth of the BOP stack—and must be carefullycontrolled to ensure proper operation of the rams. Since subseaaccumulators provide a finite and limited volume of pressurizedhydraulic fluid (between charges), it is generally desirable to conservepressurized hydraulic fluid volume within subsea accumulators.

Typically, the force required to close a ram is substantially greaterthan the force to open the ram. However, with a simple piston-cylinderassembly, the same volume of pressurized hydraulic fluid is required toopen as well as close the ram. Thus, opening the ram consumes morepressurized hydraulic fluid volume than is necessary and wastes thefinite volume of pressurized hydraulic fluid in the subsea accumulators.

Accordingly, there remains a need in the art for devices, systems, andmethods for actuating one or more rams of a subsea BOP stack. Suchdevices, systems, and methods would be particularly well-received ifthey offered the potential to reduce the volume of pressurized hydraulicfluid necessary to open the rams.

BRIEF SUMMARY OF THE DISCLOSURE

These and other needs in the art are addressed in one embodiment by avalve for controlling the flow of a fluid. In an embodiment, the valvecomprises a housing having a longitudinal axis and including a firstchamber, a second chamber, and a neutral chamber positioned axiallybetween the first chamber and the second chamber. In addition, the valvecomprises an elongate stem slidingly disposed within the housing andextending axially through the neutral chamber. The stem includes a firstend and a second end opposite the first end. Further, the valvecomprises a first valve member at least partially disposed in the firstchamber and connected to the first end of the stem. The first valvemember has a closed position seated in a first annular valve seatpositioned axially between the first chamber and the neutral chamber andan open position spaced apart from the first valve seat. Still further,the valve includes a second valve member at least partially disposed inthe second chamber and connected to the second end of the stem. Thesecond valve member has a closed position seated in a second annularvalve seat positioned axially between the second chamber and the neutralchamber and an open position spaced apart from the second valve seat.Moreover, the valve includes a biasing member positioned between thesecond valve member and the housing. The biasing member is configured tobias the second valve member to the closed position and the first valvemember to the open position.

These and other needs in the art are addressed in another embodiment bya system for drilling a subsea wellbore. In an embodiment, the systemcomprises a BOP including a main bore and a ram BOP. The ram BOPincludes a pair of opposed rams, each ram having an open positionwithdrawn from the main bore and a closed position extending into themain bore. In addition, the system comprises an actuator assemblyconfigured to transition one ram between the open position and theclosed position. The actuator assembly comprises a cylinder having aninner cavity. Further, the actuator assembly comprises a pistonslidingly disposed in the cylinder. The piston divides the inner cavityof the cylinder into a close chamber, an open chamber, and a neutralchamber positioned between the open chamber and the closed chamber.Still further, the actuator assembly comprises a connecting rod coupledto the piston and the ram. The actuator assembly also comprises a valveincluding a housing having a longitudinal axis and including a closechamber, a open chamber, and an neutral chamber positioned axiallybetween the first chamber and the second chamber. The close chamber isin fluid communication with the close chamber, the open chamber is influid communication with the open chamber, and the neutral chamber is influid communication with the neutral chamber. In addition, the valvecomprises a first valve member at least partially disposed in the closechamber and having an open position allowing fluid communication betweenthe close chamber and the neutral chamber and a closed positionpreventing fluid communication between the close chamber and the neutralchamber. Further, the valve comprises a first valve member at leastpartially disposed in the open chamber and having an open positionallowing fluid communication between the open chamber and the neutralchamber and a closed position preventing fluid communication between theopen chamber and the neutral chamber.

These and other needs in the art are addressed in another embodiment bya method for actuating a device between a first position and a secondposition. In an embodiment, the method comprises supplying pressurizedfluid through a first fluid circuit to a first chamber of apiston-cylinder assembly and a first chamber of a valve. In addition,the method comprises exhausting fluid in a second chamber of thepiston-cylinder assembly into a second fluid circuit while supplyingpressurized fluid through the first fluid circuit. Further, the methodcomprises exhausting fluid in a second chamber of the valve into thesecond fluid circuit while supplying pressurized fluid through the firstfluid circuit. Still further, the method comprises exhausting fluid in athird chamber of the piston-cylinder assembly into a third chamber ofthe valve while supplying pressurized fluid through the first fluidcircuit. Moreover, the method comprises exhausting fluid in the thirdchamber of the valve into the second chamber of the valve whilesupplying pressurized fluid through the first fluid circuit.

Embodiments described herein comprise a combination of features andadvantages intended to address various shortcomings associated withcertain prior devices, systems, and methods. The various characteristicsdescribed above, as well as other features, will be apparent to thoseskilled in the art upon reading the following detailed description andby referring to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

For a detailed description of the preferred embodiments of theinvention, reference will now be made to the accompanying drawings inwhich:

FIG. 1 is a perspective view of an embodiment of a valve in accordancewith the principles described herein;

FIG. 2 is a top view of the valve of FIG. 1;

FIG. 3 is an end view of the valve of FIG. 1;

FIG. 4 is a perspective cross-sectional view of the valve of FIG. 1taken along line A-A of FIG. 2;

FIG. 5 is a cross-sectional side view of the valve of FIG. 1 taken alongline A-A of FIG. 2 and in a close position;

FIG. 6 is a cross-sectional side view of the valve of FIG. 1 taken alongline A-A of FIG. 2 and in an open position;

FIG. 7 is a cross-sectional side view of the valve of FIG. 1 taken alongline B-B of FIG. 3;

FIG. 8 is a schematic view of an offshore drilling and/or productionsystem including a subsea BOP stack;

FIG. 9 is an enlarged schematic view of the BOP stack of FIG. 8;

FIG. 10 is a schematic view of one ram actuator assembly of the BOPstack of FIG. 9 closing one exemplary BOP ram of FIG. 9; and

FIG. 11 is a schematic view of the ram actuator assembly of FIG. 10opening the exemplary BOP ram of FIG. 10.

DETAILED DESCRIPTION OF EMBODIMENTS

The following discussion is directed to various exemplary embodiments.However, one skilled in the art will understand that the examplesdisclosed herein have a broad application, and that the discussion ofany embodiment is meant only to be exemplary of that embodiment, and notintended to suggest that the scope of the disclosure, including theclaims, is limited to that embodiment.

Certain terms are used throughout the following description and claimsto refer to particular features or components. As one skilled in the artappreciates, different persons may refer to the same feature orcomponent by different names. This document does not intend todistinguish between components or features that differ in name but notfunction. The drawing figures are not necessarily to scale. Certainfeatures and components may be shown exaggerated in scale or in somewhatschematic form and some details of conventional elements may not beshown in interest of clarity and conciseness.

In the following discussion and in the claims, the terms “including” and“comprising” are used in an open-ended fashion, and thus should beinterpreted to mean “including, but not limited to . . . .” Also, theterm “couple” or “couples” is intended to mean either an indirect ordirect connection. Thus, if a first device couples to a second device,that connection may be through a direct connection, or through anindirect connection via other devices, components, and connections. Inaddition, as used herein, the terms “axial” and “axially” generally meanalong or parallel to a central axis (e.g., central axis of a body or aport), while the terms “radial” and “radially” generally meanperpendicular to the central axis. For instance, an axial distancerefers to a distance measured along or parallel to the central axis, anda radial distance means a distance measured perpendicular to the centralaxis.

Referring now to FIGS. 1-7, an embodiment of a valve 10 in accordancewith the principles described herein. In general, valve 10 is designedand configured to control the flow of pressurized fluid (e.g.,pressurized hydraulic fluid) used to transition or actuate a device suchas a BOP ram or wedgelock between two different positions (e.g., openand closed positions). In this embodiment, valve 10 includes a valvebody or housing 20, a valve stem 50 slidingly disposed in housing 20, afirst valve member 70 connected to one end of stem 50, and a secondvalve member 80 connected to the opposite end of stem 50.

Housing 20 has a central or longitudinal axis 25, a first end 20 a, anda second end 20 b opposite end 20 a. In addition, housing 20 includesthree coaxially-aligned, axially-spaced internal cavities or chambers—aclose chamber 21, an open chamber 22, and a neutral chamber 23 axiallydisposed between chambers 21, 22. As best shown in FIGS. 5 and 6, inthis embodiment, each chamber 21, 22, 23 is defined by a radially outercylindrical surface 21 a, 22 a, 23 a, respectively, and planar endsurfaces 21 b, c; 22 b, c; 23 b, c, respectively. Surfaces 21 a, 22 a,23 a are each oriented generally parallel to axis 25, and surfaces 21 b,c; 22 b, c; 23 b, c are each oriented generally perpendicular to axis25. A close port 26 extends radially through housing 20 to close chamber21, an open port 27 extends radially through housing 20 to open chamber22, and a neutral port 28 extends radially through housing 20 to neutralchamber 23.

Referring now to FIGS. 4-7, a first annular divider or wall 30 isaxially positioned between and physically separates chambers 21, 23, anda second annular divider or wall 40 is axially positioned between andphysically separates chambers 22, 23. In particular, wall 30 extendsradially inward relative to surfaces 21 a, 23 a and defines planarsurfaces 21 c, 23 b; and wall 40 extends radially inward relative tosurfaces 22 a, 23 a and defines surfaces 22 b, 23 c. In addition, wall30 includes a cylindrical recess or counterbore 31 extending axiallyfrom surface 21 c, a central hole or bore 32 extending axially fromrecess 31 to surface 23 b, and a plurality of circumferentially spacedholes or bores 33 extending axially from recess 31 to surface 23 b.Counterbore 31 and central bore 32 are coaxially aligned within housing20, and bores 33 are disposed about central bore 32. Stem 50 extendsaxially through counterbore 31 and central bore 32. The diameter ofcentral bore 32 is substantially the same or slightly greater than thediameter of stem 50, and thus, stem 50 slidingly engages central bore32. However, counterbore 31 has a diameter greater than the outerdiameter of stem 50, and thus, an annulus 34 is formed withincounterbore 31 radially between stem 50 and wall 30. Bores 33 extendfrom annulus 34 to chamber 23, thereby allowing fluid communicationbetween annulus 34 and chamber 23.

An annular shoulder 36 is formed at the intersection of chamber 21 andcounterbore 31. In this embodiment, shoulder 36 comprises afrusto-conical surface oriented at an acute angle relative to axis 25.As will be described in more detail below, valve member 70 moves intoand out of sealing engagement with frusto-conical shoulder 36, and thus,shoulder 36 may also be referred to as a valve seat. When valve member70 is seated in valve seat 36, valve member 70 restricts or preventsfluid communication between chambers 21, 23 via annulus 34 and bores 33,however, when valve member 70 is not seated against valve seat 36, fluidcommunication between chambers 21, 23 is permitted via annulus 34 andbores 33. Thus, annulus 34 and bores 33 provide a fluid passage betweenchambers 21, 23 when valve member 70 is spaced from valve seat 36.

Referring now to FIGS. 4-7, wall 40 includes a cylindrical recess orcounterbore 41 extending axially from surface 22 b, a central hole orbore 42 extending axially from recess 41 to surface 23 c, and aplurality of circumferentially spaced holes or bores 43 extendingaxially from recess 41 to surface 23 c. Counterbore 41 and central bore42 are coaxially aligned within housing 20, and bores 43 are disposedabout central bore 42. Stem 50 extends axially through counterbore 41and central bore 42. The diameter of central bore 42 is substantiallythe same or slightly greater than the diameter of stem 50, and thus,stem 50 slidingly engages central bore 42. However, counterbore 41 has adiameter greater than the outer diameter of stem 50, and thus, anannulus 44 is formed within counterbore 41 radially between stem 50 andwall 40. Bores 43 extend from annulus 44 to chamber 23, thereby allowingfluid communication between annulus 44 and chamber 23.

An annular shoulder 46 is formed at the intersection of chamber 22 andcounterbore 41. In this embodiment, shoulder 46 comprises afrusto-conical surface oriented at an acute angle relative to axis 25.As will be described in more detail below, valve member 80 moves intoand out of sealing engagement with frusto-conical shoulder 46, and thus,shoulder 46 may also be referred to as a valve seat. When valve member80 is seated in valve seat 46, valve member 80 restricts or preventsfluid communication between chambers 22, 23 via annulus 44 and bores 43,however, when valve member 80 is not seated against valve seat 46, fluidcommunication between chambers 22, 23 is permitted via annulus 44 andbores 43. Thus, annulus 44 and bores 43 provide a fluid passage betweenchambers 22, 23 when valve member 80 is spaced from valve seat 46.

Referring again to FIGS. 1-7, in this embodiment, housing 20 is formedby a first valve block 11, a second valve block 12, a first end cap 13,and a second end cap 14 coaxially aligned and axially coupledend-to-end. End cap 13 and block 11 define close chamber 21; blocks 11,12 define neutral chamber 23; and end cap 14 and block 12 define openchamber 22. As best shown in FIGS. 1, 3, and 7, a plurality ofcircumferentially-spaced throughbores 15 extend axially through eachblock 11, 12 and cap 13, 14 between ends 20 a, b. Bolts (not shown) arepassed through bores 15 to axially compress housing 20 and hold blocks11, 12 and end caps 13, 14 together. An annular seal assembly 16 isradially disposed between and sealingly engages end cap 13 and block 11,an annular seal assembly 17 is radially disposed between and sealinglyengages blocks 11, 12, and an annular seal assembly 18 is radiallydisposed between and sealingly engages end cap 14 and block 12. In thisembodiment, each seal assembly 16, 17, 18 comprises an annular recess orseal gland and an O-ring seal disposed in the seal gland. Sealassemblies 16, 17, 18 restrict or prevent fluid communication throughthe joints formed between blocks 11, 12 and end caps 13, 14.

Referring now to FIGS. 4-7, stem 50 is an cylindrical rod coaxiallydisposed in housing 20. As previously described, stem 50 extends throughand slidingly engages central bores 33, 43 in walls 30, 40,respectively. In addition, stem 50 has a central or longitudinal axis 55coincident with axis 25, a first end 50 a proximal to close chamber 21,and a second end 50 b opposite end 50 a and proximal to open chamber 22.In this embodiment, stem 50 is made from two separate elongate stemsthat are connected end-to-end with a threaded stud.

Ends 50 a, b are secured to valve members 70, 80, respectively. In thisembodiment, valve members 70, 80 are integral and monolithically formedwith respective ends 50 a, b. Each valve member 70, 80 is an annulardisc coaxially aligned with stem 50. In particular, each valve member70, 80 has an inner end 70 a, 80 a, respectively, integral with end 50a, b, respectively, and an outer end 70 b, 80 b, respectively, integralwith distal end 50 a, b, respectively. In addition, each valve member70, 80 comprises a frustoconical surface 71, 81, respectively, extendingfrom inner end 70 a, 80 a, respectively. Surfaces 71, 81 are oriented atan acute angle relative to axes 25, 55, and more specifically, areoriented at the same angle as valve seat 36, 46, respectively. Thus,surfaces 71, 81 of valve members 70, 80, respectively, are configured tomate with valve seats 36, 46, respectively. Each valve member 70, 80also includes a cylindrical recess or counterbore 72, 82, respectively,extending axially from outer end 70 b, 80 b, respectively.

Valve member 70 releasably engages mating valve seat 36 to control fluidcommunication between close chamber 21 and neutral chamber 23, and valvemember 80 releasably engages mating valve seat 46 to control fluidcommunication between open chamber 22 and neutral chamber 23.Frustoconical surface 71 of valve member 70 mates with seat 36, therebyforming an annular metal-to-metal seal 74 therebetween when valve member70 engages seat 36. Likewise, frustoconical surface 81 of valve member80 mates with seat 46, thereby forming an annular metal-to-metal seal 84therebetween when valve member 80 engages seat 46. Seal 74 restrictsand/or prevents fluid communication between close chamber 21 and annulus34 when valve member 70 is seated in seat 36, and seal 84 restrictsand/or prevents fluid communication between open chamber 22 and annulus44 when valve member 80 is seated in seat 46. Accordingly, each valvemember 70, 80 may be described as having a closed position engaging seat36, 46, respectively, and an open position axially spaced from seat 36,46, respectively.

Stem 50 moves axially within housing 20 to move valve members 70, 80into and out of sealing engagement with mating seats 36, 46,respectively (i.e., between the open and closed positions). In otherwords, valve members 70, 80 move axially relative to housing 20 alongwith stem 50. In particular, stem 50 has an axial length such that whenvalve member 80 is in the closed position sealingly engaging seat 46,valve member 70 is in the open position axially spaced from seat 36(FIG. 5); and when valve member 70 is in the closed position sealinglyengaging seat 36, valve member 80 is in the open position axially spacedfrom seat 46 (FIG. 6). Thus, when fluid communication between chambers22, 23 is restricted and/or prevented by seal 84 between valve member 80and seat 46, fluid communication between chambers 21, 23 is permitted(FIG. 5); and when fluid communication between chambers 21, 23 isrestricted and/or prevented by seal 74 between valve member 70 and seat36, fluid communication between chambers 22, 23 is permitted (FIG. 6).It should be appreciated that one valve member 70, 80 is open when theother valve member 70, 80 is closed, and further, neutral chamber 23 isin fluid communication with chamber 21 or chamber 22 depending on whichvalve member 70, 80 is open.

Valve member 80 is biased to the closed position engaging seat 46 by abiasing member 87 positioned axially between valve member 80 and housing20. Since valve member 70 is in the open position when valve member 80is in the closed position, biasing member 87 may also be described asbiasing valve member 70 to the open position. In this embodiment,biasing member 87 is a coil spring. Biasing member 87 is seated inrecess 82 of valve member 80 to restrict and/or prevent biasing member87 from moving radially within chamber 22.

Referring still to FIGS. 5 and 6, the axial positions of stem 50 andvalve members 70, 80 depends on the combined effects of the biasingforce applied by biasing member 87 and the fluid pressures withinchambers 21, 22. As previously described, one valve member 70, 80 isopen when the other valve member 70, 80 is closed, and neutral chamber23 is in fluid communication with chamber 21 or chamber 22 depending onwhich valve member 70, 80 is open. Thus, the fluid pressure in neutralchamber 23 will typically be the same as the fluid pressure of thechamber 21, 22 that is in fluid communication with neutral chamber 23.The fluid pressure within each chamber 21, 22 is controlled via ports26, 27.

When the sum of the axial forces applied to valve member 80 by biasingmember 87 and fluid pressure within chamber 22 are greater than the sumof the axial forces applied to valve member 70 by fluid pressure withinchamber 21 and the fluid pressure applied to valve member 80 by fluidpressure within annulus 44, valve member 80 will remain in the closedposition and valve member 70 will remain in the open position. As aresult, chambers 21, 23 will remain in fluid communication, and chamber22 will not be in fluid communication with chambers 21, 23. However,when the sum of the axial forces applied to valve member 80 by biasingmember 87 and fluid pressure within chamber 22 are less than the sum ofthe axial forces applied to valve member 70 by fluid pressure withinchamber 21 and the fluid pressure applied to valve member 80 by fluidpressure within annulus 44, valve member 80 will transition to the openposition and valve member 70 will transition to the closed position. Asa result, chambers 22, 23 will be in fluid communication, and chamber 21will not be in fluid communication with chambers 22, 23. Valves 70, 80will transition back to the open and closed positions, respectively,when the sum of the axial forces applied to valve member 80 by biasingmember 87 and fluid pressure within chamber 22 are greater than the sumof the axial forces applied to valve member 70 by fluid pressure withinchamber 21 and the fluid pressure applied to valve member 80 by fluidpressure within annulus 44. The biasing force applied by biasing member87 is predetermined and generally constant, and thus, by varying thefluid pressure differential between chambers 21, 22, valve members 70,80 may be transitioned between the open and closed positions.

Valve 10 is particular designed and suited to control the flow ofpressurized fluid (e.g., pressurized hydraulic fluid) used to transitionor actuate a device or component (e.g., BOP rams or wedgelocks) betweentwo different positions (e.g., open and closed positions, locked andunlocked, first position and second position, etc.). In suchapplications, valve 10 offers the potential to more efficiently utilizestored fluid pressure and reduce reliance on hydraulic accumulators ascompared to conventional hydraulically actuated devices.

Referring now to FIG. 8, an embodiment of an offshore system 100 fordrilling and producing a wellbore 101 is shown. In this embodiment,system 100 includes an offshore vessel or platform 105 at the seasurface 102 and a subsea-BOP-stack assembly 110 mounted to a wellhead140 at the sea floor 103. Platform 105 is equipped with a derrick 106that supports a hoist (not shown). A tubular drilling riser 104 extendsfrom platform 105 to BOP stack assembly 110. Riser 104 returns drillingfluid or mud to platform 105 during drilling operations. Casing 107extends from wellhead 140 into subterranean wellbore 101.

Downhole operations are carried out by a tubular string 108 (e.g.,drillstring, production tubing string, coiled tubing, etc.) that issupported by derrick 106 and extends from platform 105 through riser104, through the BOP-stack assembly 110, and into the wellbore 101. Adownhole tool 109 is connected to the lower end of tubular string 108.In general, downhole tool 109 may comprise any suitable downhole tool(s)for drilling, completing, evaluating, or producing wellbore 101including, without limitation, drill bits, packers, testing equipment,perforating guns, and the like. During downhole operations, string 108,and tool 109 coupled thereto, may move axially, radially, orrotationally relative to riser 104 and BOP stack assembly 110.

Referring now to FIGS. 8 and 9, BOP stack assembly 110 is mounted towellhead 140 and is designed and configured to control and seal wellbore101, thereby containing the hydrocarbon fluids therein. In thisembodiment, BOP stack assembly 110 comprises an LMRP 120 and a BOP stack130. BOP stack 130 is mounted to wellhead 140, and LMRP 120 is securedto the upper end of BOP stack 130 and the lower end of riser 104. Inthis embodiment, the connections between wellhead 140, BOP stack 130,and LMRP 120 comprise mechanical wellhead-type connections 150. Ingeneral, connections 150 may comprise any suitable releasablewellhead-type mechanical connection such as the H-4® profile subseasystem available from VetcoGray Inc. of Houston, Tex. and the DWHCprofile subsea system available from Cameron International Corporationof Houston, Tex. Typically, such hydraulically actuated, mechanicalwellhead-type connections (e.g., connections 150) comprise anupward-facing male connector or hub that is received by and releasablyengages a downward-facing mating female connector or receptacle.

Referring still to FIGS. 8 and 9, LMRP 120 comprises a riser flex joint121, a riser adapter 122, and an annular BOP 123. A flow bore 125extends through LMRP 120 from riser 104 at the upper end of LMRP 120 toconnection 150 at the lower end of LMRP 120. Riser adapter 122 extendsupward from flex joint 121 and is coupled to the lower end of riser 104with a flange joint. Flex joint 121 allows riser adapter 122 and riser104 connected thereto to deflect angularly relative to LMRP 120 whilehydrocarbon fluids flow from wellbore 101 through BOP stack assembly 110into riser 104. Annular BOP 123 comprises an annular elastomeric sealingelement that is mechanically squeezed radially inward to seal on atubular extending through LMRP 120 (e.g., string 108, casing, drillpipe,drill collar, etc.) or seal off bore 125. Thus, annular BOP 123 has theability to seal on a variety of pipe sizes and seal off bore 125 when notubular is extending therethrough.

BOP stack 130 comprises a plurality of axially-stacked ram BOPs 131. Amain bore 133 extends through BOP stack 130 from LMRP 120 at the upperend of stack 130 to wellhead 140. Each ram BOP 131 includes a pair ofopposed rams and a pair of actuator assemblies 200 that actuate anddrive the matching rams—one actuator assembly 200 controls the positionof one of the pair of opposed rams. In this embodiment, BOP stack 130includes three ram BOPs 131; (1) an upper-ram BOP 131 including opposedblind shear rams or blades 131 a for severing tubular string 108 andsealing off wellbore 101 from riser 104 (or sealing off wellbore 101when no string or tubular extends through bore 133); (2) oneintermediate-ram BOP 131 including opposed blind shear rams 131 a forsevering tubular string 108 and sealing off wellbore 101 from riser 104(or sealing off wellbore 101 when no string or tubular extends throughbore 133); and (3) one lower-ram BOP 131 including opposed pipe rams 131c for engaging string 108 and sealing the annulus around tubular string108.

Opposed rams 131 a, c are located in cavities that intersect main bore133 and support rams 131 a, c as they move into and out of main bore133. Each set of rams 131 a, c is actuated and transitioned between anopen position and a closed position by corresponding actuator assemblies200. In the open positions, rams 131 a, c are radially withdrawn frommain bore 133. However, in the closed positions, rams 131 a, c areradially advanced into main bore 133 to close off and seal main bore 133(e.g., rams 131 a) or the annulus around tubular string 108 (e.g., 131c). Main bore 133 is coaxially aligned with flow bore 125 of LMRP 120,and is in fluid communication with flow bore 125 when rams 131 a, c areopen.

As previously described, in this embodiment, BOP stack 130 includesthree sets of ram BOPs (two sets of blind-shear rams 131 a and one setof pipe rams 131 c). However, in other embodiments, the BOP stack (e.g.,stack 130) may include different numbers of rams, different types oframs, an annular BOP (e.g., annular BOP 123), or combinations thereof.Further, although LMRP 120 is shown and described as including oneannular BOP 123, in other embodiments, the LMRP (e.g., LMRP 120) mayinclude a different number of annular BOPs (e.g., two sets of annularBOPs 123). Moreover, although BOP stack 130 may be referred to as astack since it contains a plurality of ram BOPs 131 in this embodiment,in other embodiments, BOP stack 130 may include only one ram BOP 131.

Referring now to FIGS. 10 and 11, one actuator assembly 200 of one BOPram 131 of FIG. 9 is shown. Here, actuator assembly 200 is showntransitioning an exemplary ram 131 a of a pair of opposed rams betweenthe open and closed positions. More specifically, in FIG. 10, actuatorassembly 200 is shown transitioning ram 131 a from the open positionradially withdrawn from main bore 133 to the closed position radiallyadvanced into main bore 133; and in FIG. 11, actuator assembly 200 isshown transitioning ram 131 a from the closed position radially advancedinto main bore 133 to the open position radially withdrawn from mainbore 133. Although actuator assembly 200 is shown transitioning anexemplary shear ram 131 a, in general, actuator assembly 200 may beemployed to actuate any type of ram (e.g., shear blind ram 131 a, piperam 131 c, etc.) or any type of device between two different positions.For example, actuator assembly 200 shown in FIGS. 10 and 11 is employedwith each of the rams 131 a, 131 c shown in FIG. 9.

In this embodiment, actuator assembly 200 includes a piston-cylinderassembly 210 and valve 10 previously described. Piston-cylinder assembly210 includes a housing or cylinder 220 and a piston 230 slidinglydisposed in cylinder 220. Cylinder 220 has a central axis 225, a firstend 220 a distal main bore 133, a second end 220 b opposite end 220 aand proximal main bore 133, and an inner chamber or cavity 221 extendingaxially between ends 220 a, b. In this embodiment, an annular planarshoulder 222 divides cavity 221 into a first or increased diametersection 221 a extending axially from end 220 a to shoulder 222 and asecond or reduced diameter section 221 b extending axially from end 220b to shoulder 222. First section 221 a of cavity 221 has a uniformradius R_(221a), and second section 221 b of cavity 221 has a uniformradius R_(221b) that is less than radius R_(221a).

Piston 230 is coaxially disposed within cylinder 220 and has a first end230 a distal main bore 133 and a second end 230 b opposite end 230 a andproximal main bore 133. In this embodiment, an annular planar shoulder232 divides piston 230 into a first or increased diameter section 231 aextending axially from end 230 a to shoulder 232 and a second ordecreased diameter section 231 b extending axially from end 230 b toshoulder 232. First section 231 a of piston 230 has a uniform radiusR_(231a), and second section 231 b of piston 230 has a uniform radiusR_(231b) that is less than radius R_(221a). In addition, radius R_(231a)is substantially the same or slightly less than radius R_(221a), andthus, first section 231 a of piston 230 slidingly engages cylinder 220within first section 221 a of cavity 221; and radius R_(231b) issubstantially the same or slightly less than radius R_(221b), and thus,second section 231 b of piston 230 slidingly engages cylinder 220 withinsecond section 221 b of cavity 221. It should be appreciated that radiusR_(231a) is greater than radius R_(221b), and thus, first section 231 aof piston 230 does not fit within second section 221 b of cavity 221;and further, radius R_(231b) is less than radius R_(221a), and thus,second section 231 b of piston 230 can fit within first section 221 a ofcavity 221 but does not slidingly engage cylinder 220 within firstsection 221 a.

Referring still to FIGS. 10 and 11, piston 230 divides cavity 221 ofcylinder 220 into three volumes or chambers: (1) a first chamber 223extending axially from end 220 a to section 231 a of piston 230; (2) asecond chamber 224 extending axially from section 231 a of piston 230 toshoulder 222; and (3) a third chamber 225 extending axially from end 220b to section 231 b of piston 230. Chamber 225 is an annulus radiallypositioned between second section 231 b of piston 230 and cylinder 220.

Chambers 223, 224, 225 are sealed from one another withinpiston-cylinder assembly 210. More specifically, in this embodiment, afirst annular seal assembly 236 is radially disposed between section 231a of piston 230 and cylinder 220, and a second annular seal assembly 237is radially positioned between section 231 b of piston 230 and cylinder220. Each seal assembly 236, 237 includes an annular gland in section231 a, 231 b, respectively, of piston 230 and an annular-seal memberdisposed in gland 236 a, 237 a, respectively. Each seal member forms astatic seal with piston 230 within its corresponding gland and a dynamicseal with cylinder 220. Accordingly, seal assembly 236 restricts orprevents fluid communication between chambers 223, 224, and sealassembly 237 restricts or prevents fluid communication between chambers224, 225.

As will be described in more detail below, ram 131 a is transitioned tothe closed position by increasing the fluid pressure in first chamber223 relative to the fluid pressure in chambers 224, 225, and ram 131 ais transitioned to the open position by increasing the fluid pressure inthird chamber 225 relative to the fluid pressure in chambers 223, 224.Thus, first chamber 223 may also be referred to as the close chamber,and third chamber 225 may also be referred to as the open chamber.Further, since chamber 224 is in fluid communication with neutralchamber 23 of valve 10, it may also be referred to as a neutral chamber.A first port 223 a extends through cylinder 220 and is in fluidcommunication with close chamber 223, a second port 224 a extendsthrough cylinder 220 and is in fluid communication with chamber 224, anda third port 225 a extends through cylinder 220 and is in fluidcommunication with open chamber 225.

Second end 230 b of piston 230 is coupled to ram 131 a with an elongateconnecting rod 240 that extends axially through end 220 b of cylinder220. In particular, rod 240 slidingly engages a throughbore 226 in end220 b of cylinder 220. Ram 131 a is fixed to one end of rod 240 andsecond section 231 b of piston 230 is fixed to the opposite end of rod240. Thus, rod 240 and ram 131 a do not move rotationally ortranslationally relative to piston 230, and ram 131 a moves axiallyalong with piston 230.

An annular-seal assembly 227 is radially disposed between rod 240 andcylinder 220 along through bore 226. Seal assembly 227 includes anannular recess or gland and an annular seal member disposed in thegland. The seal member forms a static seal with cylinder 220 and adynamic seal with rod 240. Accordingly, seal assembly 227 restricts orprevents fluid flow through bore 226 between rod 240 and cylinder 220.

Referring still to FIGS. 10 and 11, a first fluid circuit 250 includes afluid supply/exhaust line 251 coupled to port 223 a and port 26. Thus,fluid line 251 is in fluid communication with both close chamber 223 ofpiston-cylinder assembly 210 via port 223 a and chamber 21 of valve 10via port 26. Similarly, a second fluid circuit 260 includes a fluidsupply/exhaust line 261 coupled to port 225 a and port 27. Thus, fluidsupply/exhaust line 261 is in fluid communication with chamber 225 ofpiston-cylinder assembly 210 via port 225 a and chamber 22 of valve 10via port 27. Still further, a fluid line 270 has one end coupled to port224 a and the opposite end coupled to port 28. Thus, fluid line 270 isin fluid communication with chamber 224 of piston-cylinder assembly 210via port 224 a and chamber 23 of valve 10 via port 28. In general, fluid(e.g., hydraulic fluid) may be supplied to or exhausted from chambers21, 223 simultaneously via first fluid circuit 250, and fluid may besupplied to or taken from chambers 22, 225 simultaneously via secondfluid circuit 260. Fluid line 270 simply allows fluid to flow betweenchambers 23, 224.

Referring now to FIG. 10, to move ram 131 a radially inward relative tobore 133 (i.e., transition ram 131 a to the closed position),pressurized fluid represented by arrows 280 (e.g., pressurized hydraulicfluid) is simultaneously supplied to close chamber 21 of valve 10 andclose chamber 223 of piston-cylinder assembly 210 via first fluidcircuit 250. In general, pressurized fluid 280 may be supplied tocircuit 250 by any suitable source including, without limitation, a pumpor fluid accumulators. In this embodiment, pressurized fluid 280 issupplied to circuit 250 by one or more subsea hydraulic fluidaccumulators connected to line 251 or from vessel 105 via one or morehydraulic lines extending subsea to line 251. Pressurized fluid 280 inchamber 223 of piston-cylinder assembly 210 begins to force piston 230in a first axial direction 290 through cylinder 220 (to the right inFIG. 10). In addition, pressurized fluid 280 in chamber 21 of valve 10transitions valve member 70 from the biased open position to the closedposition, thereby transitioning valve member 80 from the biased closedposition to the open position. Prior to closing valve member 70 andopening valve member 80, chamber 21 of valve 10 is in fluidcommunication with chamber 23 via annulus 34 and bores 33, and chamber23 of valve 10 is in fluid communication with chamber 224 ofpiston-cylinder assembly 210 via line 270. Thus, the fluid pressure inchamber 224 is substantially the same as the fluid pressure in chamber223, and resists the axial movement of piston 230 through cylinder 220in first axial direction 290, thereby hydraulically locking piston 230.However, once valve member 70 is closed and valve member 80 is open,piston 230 is no longer hydraulically locked since chambers 23, 224 areno longer in fluid communication with first fluid circuit 250 andchamber 21; instead, chambers 23, 224 are in fluid communication withchamber 22 of valve 10 via bores 43 and annulus 44 and circuit 260 viaport 27. Thus, as piston 230 is moved axially in first direction 290 byfluid pressure within chamber 223, fluid in chambers 224, 225represented by arrows 281 (e.g., hydraulic fluid) is exhausted intocircuit 260, where it may be vented or recycled. In particular, fluid inopen chamber 225 flows into circuit 260, fluid in chamber 224 flows intochamber 23 of valve 10, fluid in chamber 23 flows into open chamber 22of valve 10, and fluid in chamber 22 flows into circuit 260. As piston230 continues to be pushed in the first axial direction 290, shear ram131 a moves radially into main bore 133 and transitions to the closedposition.

Referring now to FIG. 11, to radially withdraw ram 131 a from bore 133(i.e., transition ram 131 a to the open position), close chamber 21 ofvalve 10 and close chamber 223 of piston-cylinder assembly 210 arevented via first fluid circuit 250, thereby allowing biasing member 87to bias valve member 80 to the closed position and valve member 70 tothe open position. Thus, chambers 23, 224 are in fluid communicationwith chamber 21 of valve 10 via bores 33 and annulus 34 and circuit 250via port 26, and chamber 22 is isolated from chambers 23, 224. Next,pressurized fluid 280 (e.g., pressurized hydraulic fluid) issimultaneously supplied to open chamber 22 of valve 10 and open chamber225 of piston-cylinder assembly 210 via supply/exhaust line 261. Ingeneral, pressurized fluid 280 may be supplied to circuit 260 by anysuitable source including, without limitation, a pump or fluidaccumulators. In this embodiment, pressurized fluid 280 is supplied tocircuit 260 by one or more subsea hydraulic fluid accumulators connectedto line 261 or from vessel 105 via one or more hydraulic lines extendingsubsea to line 261.

As piston 230 is moved axially in second direction 291 by fluid pressurewithin chamber 225, fluid 281 in chamber 223 is exhausted into circuit250, fluid in chamber 23 is pulled into chamber 224, fluid in chamber 21is pulled into chamber 23, and fluid in circuit 250 is pulled intochamber 21. The volume of fluid 281 in chamber 223 displaced by piston230 is greater than the volume of fluid 281 pulled into chamber 224 dueto the presence of piston section 231 b extending through chamber 224and occupying volume therein. Accordingly, more fluid 281 is exhaustedinto circuit 250 than is pulled from circuit 250 into chamber 21. Thenet excess fluid 281 exhausted into circuit 250 may be vented orrecycled via line 251. As piston 230 continues to be pushed in thesecond axial direction 291, shear ram 131 a is radially withdrawn frommain bore 133 and transitions to the open position. In the mannerdescribed, application of pressurized hydraulic fluid to circuit 250transitions shear ram 131 a to the closed position by pressurizing closechambers 21, 223, and application of pressurized hydraulic fluid tocircuit 260 transitions shear ram 131 a to the open position bypressurizing open chambers 22, 225.

In general, opening a ram of a ram BOP (e.g., shear ram 131 a) requiresless axial force than closing the ram due to the pressure of fluids(e.g., formation fluids) in the main bore of the BOP stack (e.g., mainbore 133 of BOP stack 130). Thus, it is typically not necessary to applythe same force to the piston to open the ram as is applied to close theram. Further, it is typically desirable to minimize the volume ofpressurized hydraulic fluid required to open and close a ram sincesupplying a sufficient volume of pressurized hydraulic fluid from thesurface to actuate a ram may be challenging, and subsea accumulatorscontain a finite and limited volume of pressurized hydraulic fluid(between charges).

Conventional ram actuators utilize the same volume of pressurizedhydraulic fluid to both open and close the ram, and substantially thesame axial force to both open and close the ram. Accordingly, mostconventional ram actuators inefficiently utilize hydraulic power—moreaxial force and hydraulic fluid volume are used to open the ram that isnecessary. To the contrary, embodiments of actuator assemblies describedherein (e.g., actuator assembly 200) offer the potential to moreefficiently utilize hydraulic power by reducing pressurized hydraulicfluid demands to open ram 131 a. In particular, the volume ofpressurized hydraulic fluid required to open ram 131 a is less than thevolume of hydraulic fluid required to close ram 131 a, and further, andthe axial force applied to piston 230 to open ram 131 a is less than theaxial force applied to piston 230 to close ram 230. This is the casebecause radii R_(221b), R_(231b) are less than radii R_(221a), R_(231a),and thus, the volume of pressurized hydraulic fluid required to movepiston 230 a given axial distance in direction 291 to open ram 131 a isless than the volume of pressurized hydraulic fluid required to movepiston 230 the same axial distance in direction 290 to close ram 131 a.By decreasing the volume of pressurized hydraulic fluid to open ram 131a, the demands placed on the pressurized hydraulic fluid supplied fromthe surface and/or by subsea accumulators to open ram 131 a is reduced.The reduction in the volume of pressurized hydraulic fluid to open ram131 a is equal to the volume of chamber 224.

One of ordinary skill appreciates that the hydraulic fluid in chamber224 is generally at the same pressure as the chamber 223, 225 with whichit is in fluid communication (i.e., chamber 225 during closing of ram131 a and chamber 223 during opening of ram 131 a). In this sense,chamber 224 may be referred to as a neutral or balance chamber. Forexample, while closing of ram 131 a, pressurized hydraulic fluid isprovided to chamber 223, valve member 70 closes and chamber 224 is influid communication with the unpressurized chamber 225; and whileopening ram 131 a, pressurized hydraulic fluid is provided to chamber225, valve member 80 closes and chamber 224 is in fluid communicationwith the unpressurized chamber 223. Thus, the pressure of hydraulicfluid in chamber 224 does not need to be controlled or regulatedindependent of chambers 223, 225; the hydraulic fluid in chamber 224merely reacts to the pressurized hydraulic fluid supplied to chamber 223or chamber 225. This eliminates the need for dedicated accumulators toprovide pressurized hydraulic fluid to chamber 224, and eliminates ahydraulic fluid storage device to: (a) supply hydraulic fluid to chamber224 when ram 131 a is opened, and (b) receive hydraulic fluid fromchamber 224 when ram 131 a is closed.

While preferred embodiments have been shown and described, modificationsthereof can be made by one skilled in the art without departing from thescope or teachings herein. The embodiments described herein areexemplary only and are not limiting. Many variations and modificationsof the systems, apparatus, and processes described herein are possibleand are within the scope of the invention. For example, the relativedimensions of various parts, the materials from which the various partsare made, and other parameters can be varied. Accordingly, the scope ofprotection is not limited to the embodiments described herein, but isonly limited by the claims that follow, the scope of which shall includeall equivalents of the subject matter of the claims.

What is claimed is:
 1. A system for drilling a subsea wellbore, the system comprising: a blowout preventor comprising a main bore and a pair of opposed rams, each ram having an open position withdrawn from the main bore and a closed position extending into the main bore; and a valve configured to facilitate actuation of the rams, the valve comprising: a housing having a longitudinal axis and including a first chamber in fluid communication with a first source of pressurized fluid to move one of the rams to the closed position, a second chamber in fluid communication with a second source of pressurized fluid to move the one of the rams to the open position, and a neutral chamber positioned axially between the first chamber and the second chamber; a first valve member and a first annular valve seat at least partially disposed in the first chamber, wherein the first valve member has a closed position seated in the first valve seat and an open position spaced apart from the first valve seat; and a second valve member and a second annular valve seat at least partially disposed in the second chamber, wherein the second valve member has a closed position seated in the second annular valve seat and an open position spaced apart from the second valve seat.
 2. The system of claim 1, wherein the valve includes a stem slidably disposed in the housing, wherein the stem has a first end connected to the first valve member and a second end connected to the second valve member.
 3. The system of claim 2, wherein the valve includes a biasing member disposed in the second chamber between the second valve member and the housing, wherein the biasing member is configured to bias the second valve member to the closed position and the first valve member to the open position.
 4. The system of claim 1, further comprising: an actuator assembly configured to transition one of the rams between the open position and the closed position, wherein the actuator assembly comprises: a cylinder having an inner cavity; a piston slidingly disposed in the cylinder, wherein the piston divides the inner cavity of the cylinder into a close chamber, an open chamber, and a neutral chamber positioned between the open chamber and the closed chamber; and a connecting rod coupled to the piston and the ram.
 5. The system of claim 1, wherein the housing includes the first annular valve seat extending axially from the first chamber and the second valve seat extending axially from the second chamber; wherein the first valve member engages the first valve seat in the closed position and is axially spaced from the first valve seat in the open position; and wherein the second valve member engages the second valve seat in the closed position and is axially spaced from the second valve seat in the open position.
 6. The system of claim 5, wherein the first valve member forms an annular metal-to-metal seal with the first valve seat in the closed position and the second valve member forms an annular metal-to-metal seal with the second valve seat in the closed position.
 7. The system of claim 6, wherein the first chamber has a diameter and the second chamber has a diameter less than the diameter of the first chamber.
 8. The system of claim 4, wherein the close chamber is in fluid communication with first chamber, the valve neutral chamber, and the cylinder neutral chamber when the first valve member is in the open position; and wherein the open chamber is in fluid communication with the second chamber, the valve neutral chamber, and the cylinder neutral chamber when the second valve member is in the open position.
 9. The system of claim 4, wherein the inner cavity has a central axis and extends axially through the cylinder between a first end and a second end, wherein the inner cavity includes a first portion having a first radius and a second portion having a second radius that is less than the first radius; wherein the piston has a first section that slidingly engages the cylinder in the first portion of the inner cavity and a second section that slidingly engages the cylinder in the second portion of the inner cavity.
 10. The system of claim 9, wherein the close chamber extends axially from the first end of the inner cavity to the first section of the piston, the open chamber extends axially from the second end of the inner cavity to the second section of the piston, and the neutral chamber is disposed about the second section of the piston and within the first portion of the inner cavity.
 11. The system of claim 8, further comprising: a first fluid circuit in fluid communication with the first chamber, the close chamber, and the first source of pressurized fluid; a second fluid circuit in fluid communication with the second chamber, the open chamber, and the second source of pressurized fluid; and a flow line extending from the cylinder neutral chamber to the valve neutral chamber.
 12. The system of claim 11, wherein at least one of the first source of pressurized fluid and the second source of pressurized fluid comprises one or more hydraulic accumulators.
 13. A method for actuating a BOP (or a ram of a BOP) between a first position and a second position, comprising: supplying pressurized fluid through a first fluid circuit to a first chamber of a piston-cylinder assembly and a first chamber of a valve; exhausting fluid in a second chamber of the piston-cylinder assembly into a second fluid circuit while supplying pressurized fluid through the first fluid circuit; exhausting fluid in a second chamber of the valve into the second fluid circuit while supplying pressurized fluid through the first fluid circuit; exhausting fluid in a third chamber of the piston-cylinder assembly into a third chamber of the valve while supplying pressurized fluid through the first fluid circuit; and exhausting fluid in the third chamber of the valve into the second chamber of the valve while supplying pressurized fluid through the first fluid circuit.
 14. The method of claim 13, further comprising preventing fluid communication between the first chamber of the valve and the third chamber of the valve.
 15. The method of claim 14, further comprising moving a valve member into engagement with a valve seat of the valve to prevent fluid communication between the first chamber of the valve and the third chamber of the valve.
 16. The method of claim 14, further comprising allowing fluid communication between the second chamber of the valve and the third chamber of the valve while supplying pressurized fluid through the first fluid circuit.
 17. The method of claim 16, further comprising moving a valve member out of engagement with a valve seat of the valve to allow fluid communication between the second chamber of the valve and the third chamber of the valve.
 18. The method of claim 13, further comprising: moving a piston of the piston-cylinder assembly in a first axial direction through a cylinder of the piston-cylinder assembly to transition a component to the first position while supplying pressurized fluid through the first fluid circuit.
 19. The method of claim 18, further comprising: supplying pressurized fluid through the second fluid circuit to the second chamber of the piston-cylinder assembly and the second chamber of the valve; exhausting fluid in the first chamber of the piston-cylinder assembly into the first fluid circuit while supplying pressurized fluid through the second fluid circuit.
 20. The method of claim 19, further comprising: pulling fluid from the third chamber of the valve into the third chamber of the piston-cylinder assembly while supplying pressurized fluid through the second fluid circuit; and pulling fluid from the first circuit into the first chamber of the valve while supplying pressurized fluid through the second fluid circuit; pulling fluid from the first chamber of the valve into the third chamber of the valve while supplying pressurized fluid through the second fluid circuit. 